Sealing valve arrangement for a shaft furnace charging installation

ABSTRACT

A sealing valve arrangement for a shaft furnace charging installation, said arrangement comprising: a shutter arranged for cooperating with a valve seat; an integrated dual-motion shutter-actuating device for moving said shutter between a sealed closed position in sealing contact with the valve seat and an open position remote from the valve seat, said integrated dual-motion shutter-actuating device comprising: a primary motion assembly for moving said shutter from said sealed closed position to an undamped position wherein the shutter is released from the valve seat; a secondary motion assembly for tilting said shutter from said undamped position to said open position remote from the valve seat, said secondary motion assembly comprising a tilting arm carrying said shutter and connected to a tilting shaft that defines an axis of rotation and a tilting shaft actuator configured to impart an angular rotation about said axis to said tilting arm; wherein said integrated dual-motion shutter-actuating device further comprises a stationary outer cylindrical sleeve, wherein said primary motion assembly comprises an inner eccentric sleeve shaft rotationally mounted within said outer cylindrical sleeve and a primary motion actuator configured to impart angular rotation to said inner eccentric sleeve shaft, the primary motion being a function of the eccentricity and angular rotation of the inner eccentric sleeve shaft; and wherein said tilting shaft of said secondary motion assembly is rotationally mounted within said inner eccentric sleeve shaft of said primary motion assembly, the secondary motion being a function of the angular rotation of the tilting shaft.

TECHNICAL FIELD

The present disclosure generally relates to a sealing valve arrangementfor a shaft furnace charging installation and more specifically to anupper or lower sealing valve arrangement for preventing furnace gas lossin a blast furnace charging installation.

BACKGROUND

Shaft furnace charging installations of the BELL LESS TOP® type havefound widespread use in industry during the last decades. An earlyexample of such an installation is disclosed e.g. in U.S. Pat. No.4,071,166. This installation minimizes escape of blast furnace gas fromthe furnace throat by operating one or more intermediate charge materialstorage hoppers in the manner of a sluice or airlock. To this effect,each hopper has an upper sealing valve and a lower sealing valve forsealing closure of the hopper inlet and outlet respectively. Duringfilling of the hopper, the upper sealing valve is open whilst the lowersealing valve is closed. When material is charged from the hopper intothe furnace, the lower sealing valve is open whilst the upper sealingvalve is closed. U.S. Pat. No. 4,071,166 discloses a commonly usedsealing valve arrangement with a flap-type valve, in which the shutteris tiltable about a single shaft. The axis of this shaft is arrangedapproximately in the plane of the valve seat. Since the shutter has tobe completely removed from the material flow path in the open position,the arrangement according to U.S. Pat. No. 4,071,166 requiresconsiderable space in the vertical direction, both inside the lowersealing valve housing and inside each intermediate storage hopper (seee.g. FIG. 1 of this patent). In other words, this valve arrangementrequires a certain free height inside the sealing valve housing andlimits the maximum filling height of the hoppers.

In order to reduce “lost” vertical constructional space, improvedso-called dual-motion shutter-actuating devices have been proposed. U.S.Pat. No. 4,514,129 proposes such a dual-motion shutter-actuating device.This device is configured to tilt the valve about a first axis and toseparately pivot the shutter together with its mounting arm about asecond axis that is perpendicular to the first axis. This dual-motionshutter-actuating device allows moving the shutter into a higher parkingposition located laterally of and partially above the seat. The valvearrangement according to U.S. Pat. No. 4,514,129 thereby considerablyreduces the required constructional height. U.S. Pat. No. 4,755,095discloses a similar shutter-actuating device in an upper sealing valvearrangement, i.e. for sealing the inlet of the hopper. A drawback ofthese types of shutter-actuating devices however lies in that they havea number of articulated parts prone to wear and exposed to harshconditions.

WO 2010/015721 A1 describes a further dual-motion lower sealing valveassembly for a shaft furnace charging installation comprising a lowersealing valve housing with a valve seat. The shutter is adapted tocooperate with the valve seat and operatively connected to a valveactuation mechanism, which can be supported by the top plate of thelower sealing valve housing, for moving the shutter into and out ofsealing contact with the valve seat. In particular, the valve actuationmechanism comprises a turn-slide cylindrical joint supporting theshutter. The cylindrical joint has a substantially vertical joint axisaccording to which the joint allows translating the shutter up and down,e.g. in vertical direction, and in a plane perpendicular to which thejoint allows swiveling the shutter, typically in a substantiallyhorizontal plane. The turn-slide cylindrical joint comprises: a shaft,acting as output shaft of the joint, an intermediate hollow sleeve, inwhich the shaft is mounted, and an outer shell, supporting the sleeveand forming the fixed frame of the joint. The shaft is axially fixed androtatable about the joint axis in the hollow sleeve. The sleeve isaxially slidable along the joint axis in the outer shell that is fixedto the housing. The mechanism further comprises a first hydrauliccylinder for axial translation (sliding) and a second hydraulic cylinderfor rotation (turning). The first cylinder has one side connected to theouter shell and the other side connected to the hollow sleeve, foraxially translating the shaft with the sleeve along the joint axisrelative to the shell. The second hydraulic cylinder has one side hingedto the sleeve and the other side hinged to the shaft in order to rotatethe shaft relative to the intermediate sleeve about the joint axis.However, again, due to the fact that the translational movement is donein a dusty environment, the life time of the mechanism is shortened dueto the fact that during actuation, dust may enter the seals and damagethe sealing surfaces. A further disadvantage of this solution is thefact that particles falling on the shutter cannot fall down.

WO 2011/000966 A1 discloses a still further dual-motionshutter-actuating device is of the type configured to confer to theshutter a superposition of two rotations about substantially paralleland offset axes, i.e. offset axes having a relative orientation closerto parallel than to perpendicular. To this effect, the device comprisesa primary tilting arm supported on a first tilting shaft, which isequipped with bearings to rotatably support the primary tilting arm on astationary structure, typically either a lower sealing valve housing oron the shell of an intermediate storage hopper, in rotatable mannerabout an immobile first axis; a secondary tilting arm that carries theshutter and is supported on a second tilting shaft, which is equippedwith bearings that rotatably support the secondary tilting arm on theprimary tilting arm, in rotatable manner about a second axis that isessentially parallel to the first axis and moves with the secondarytilting arm; and a mechanism configured to impart rotation about thesecond axis to the secondary tilting arm at the same time as the primarytilting arm rotates about the first axis. In this solution, the firsttilting shaft is configured as hollow sleeve shaft and theshutter-actuating device comprises a reference rod that extends throughthe first tilting shaft. This reference rod has a distal end portion tobe connected to a stationary structure and a proximal end portion with areference member, the mechanism having a driven side that is inengagement with the reference member. The main disadvantage of thissolution is the number of movable parts, which render the device morecostly in terms of manufacturing and assembling. Finally, the mechanismis to be operated inside a dusty environment although covered againstdust.

BRIEF SUMMARY

In view of the above, the present disclosure provides a sealing valvearrangement with a shutter-actuating device that combines reducedconstruction height with reduced number of movable parts, preferably areduced number of movable parts directly exposed to harsh conditions.

The present disclosure proposes in a first aspect a sealing valvearrangement, especially for lower or upper sealing valve arrangementsfor a charging installation of a shaft furnace, such as a blast furnace.The sealing valve arrangement comprises a shutter arranged forcooperating with a valve seat of a sealing valve and an integrateddual-motion shutter-actuating device for moving said shutter between asealed closed position in sealing contact with the valve seat and anopen position remote from the valve seat, preferably located laterallythereof. In said open position, the passage or material flow paththrough the sealing valve is entirely cleared by the shutter.

The integrated dual-motion shutter-actuating device comprises:

-   -   a primary motion assembly for moving said shutter from said        sealed closed position to an unclamped or unsealed position        wherein the shutter is released from the valve seat; and    -   a secondary motion assembly for tilting said shutter from said        unclamped or unsealed position to said open position remote from        the valve seat, said secondary motion assembly comprising a        tilting arm attached to said shutter and connected to a tilting        shaft that defines an axis of rotation and a tilting shaft        actuator configured to impart an angular rotation about said        axis to said tilting arm.

According to the present disclosure, said integrated dual-motionshutter-actuating device further comprises a stationary outercylindrical sleeve. The primary motion assembly comprises an innereccentric sleeve shaft (first eccentric sleeve shaft) rotationallymounted within said outer cylindrical sleeve and a primary motionactuator configured to impart angular rotation to said inner eccentricsleeve shaft, the primary motion being a function of the eccentricityand angular rotation of the inner eccentric sleeve shaft. Furthermore,said tilting shaft of said secondary motion assembly is rotationallymounted within said inner eccentric sleeve shaft of said primary motionassembly, the secondary motion being a function of the angular rotationof the tilting shaft.

The main advantage of the disclosure is that all parts responsible forboth primary and secondary motions of the shutter, i.e. the unclampingfrom the valve seat and the tilting away of the shutter in a parkingposition are done with an assembly having only very few andconstructionally simple parts, which are moreover easily serviceable andprotectable against dust and temperature.

As indicated above, the primary motion, in particular the distance andpath by which the shutter is moved during this primary motion, is afunction of the eccentricity and angular rotation of the inner eccentricsleeve shaft. An eccentric sleeve shaft in the context of the disclosuregenerally resembles a conventional sleeve shaft, i.e. a shaft with acentral longitudinal (coaxial) bore to hold e.g. a further shaft, exceptthat the center of the bore is not central or coaxial, but rathershifted or offset (off-center) by a distance with respect to centralaxis of the sleeve shaft. This offset distance, also termedeccentricity, will determine the maximum extent of the primary movement,i.e. the maximum distance the shutter may be moved away from the valveseat. As will be further exemplified below, this maximum distance istwice the eccentricity if the eccentric sleeve shaft is rotated by 180°.Hence, by rotating the inner eccentric sleeve shaft from a positionwhere the eccentricity position (position of the offset center of thebore or center of the shaft placed in said bore) is in a verticallyuppermost eccentricity position (shutter closed) by 180° to itslowermost position, the shutter may be entirely unclamped by a distancetwice the eccentricity. Hence, by appropriately choosing theeccentricity, the shutter may be unclamped and moved far enough from thevalve seat to be tilted away by the secondary tilting motion. Thissecondary tilting motion simply requires rotating the shaft within theeccentric bore by a sufficient angle.

It has been observed however that at least for a number of applications,wear of the valve seat and gasket is increased to an undesirable extent,if the initial unclamping of the shutter from the valve seat impliesmovements off-parallel to the valve seat's central axis.

Hence, in a further embodiment, the inner eccentric sleeve shaft isarranged within the outer cylindrical sleeve such that the eccentricityposition is located laterally by about the eccentricity distance fromthe center of the outer cylindrical sleeve when the shutter is in thesealed closed position. In other words, in such an embodiment, theprimary motion does not start from a vertically uppermost eccentricityposition, but rather from a situation where the position of theeccentric sleeve shaft is rotated by 90° with respect to the uppermostvertical position.

Remarkably, such a configuration provides an advantageous initialcomponent of the primary motion which is almost parallel to the axis ofthe valve seat, thereby allowing a comparatively gentle, wear reducingunclamping operation. In such configurations, the primary motion willimply that the inner eccentric sleeve preferably is rotated by an angleof 90°, which moves the shutter by vertical and horizontal distancesequal to the eccentricity.

Hence, even the use of only one eccentric sleeve shaft for the primarymotion allows for an initially almost translational unclamping. Thismeans that at the beginning of the opening, the movement provided by theeccentric is such that the shutter is lifted from the seat with analmost straight path, essentially parallel to the axis of the valveseat.

If desired or necessary, the translational part of the primary motionmay even be enhanced by a further constructionally simple variant of thesealing valve arrangement of the disclosure.

In such a further embodiment, the primary motion assembly furthercomprises an outer eccentric sleeve shaft (second eccentric sleeveshaft) rotationally mounted within said outer cylindrical sleeve,wherein said inner eccentric sleeve shaft (first eccentric sleeve shaft)is rotationally mounted within said outer eccentric sleeve shaft (secondeccentric sleeve shaft), the primary motion being a function of theeccentricity and angular rotation of both inner and outer eccentricsleeve shafts.

By combining two nested (first and second) eccentric sleeve shafts, eachone being rotationally movable, the primary motion can be adjusted againas a function of the eccentricity and angular rotation, but this time,of those of the inner and of the outer eccentric sleeve shaft. Theireccentricity and their rotation angle may be adapted independently tobest fit the actual situation and the objectives set by the operator. Asit will be easily understood with the examples provided below, theallowable maximum (net) distance will be twice the sum of botheccentricities if both eccentric sleeve shafts are rotated by 180°.

However, a double eccentric sleeve shaft assembly further allows aprimary motion which may be particularly advantageous or desirable incertain situations. Hence, in a still further embodiment with twoeccentric sleeve shafts, the inner and outer (first and second)eccentric sleeve shafts have the same eccentricity. Furthermore, aneccentric actuator is preferably configured to impart a simultaneouscounter-rotating angular rotation to said inner and outer eccentricsleeve shafts. In fact, by combining the same eccentricity andsimultaneous counter-rotating by the same angle of both (inner andouter) eccentric sleeve shafts, the primary motion becomes entirelytranslational without lateral shifting at any time during the primarymotion, i.e. the path of the shutter during primary motion is entirelystraight.

The primary and secondary motion may be effected by an appropriatenumber of separate actuators. In general, the use of one actuator permotion assembly will allow a convenient control without adding unduecomplexity to the sealing valve arrangement. Nevertheless, it might bedesirable or necessary to further reduce the number of parts of asealing arrangement as described herein.

Hence, in a still further embodiment, the tilting shaft actuator may bea control rod used to concomitantly rotate the tilting shaft with therotation of the inner (or outer) eccentric. In one embodiment such acontrol rod is rotationally connected with one end to a stationary pointand with the other to the tilting shaft or to a crank associatedtherewith, such that the rotating of the eccentric (primary motion) withan actuator, such as a hydraulic jack or similar, drives the rotation ofthe tilting shaft (secondary motion) by means of the control rod.

In the context of the disclosure, it is to be understood that a greaternumber of nested eccentric sleeve shafts can be used if desired ordeemed useful. In general however, the complexity of the assembly andespecially of the actuation mechanism rapidly increases with highernumbers of eccentric sleeves.

In a still further embodiment, the secondary motion of tilting theshutter to its parking position could be further assisted or completedby concomitantly or subsequently to the secondary tilting motion alsorotating the eccentric sleeve shaft (or any or more of them if present)by a further angle. For example, by rotating the eccentricityposition(s) of the eccentric sleeve shaft(s) to the side of the parkingposition, the shutter may be placed still further away from the centerof the valve as it would by only the secondary motion.

Although above only the shutter opening operation has been described, itis clear to the skilled person that closing the shutter basicallyimplies reverting the steps described for opening, it being understoodthat slightly departing from the exact reverse order may be consideredif desired.

The tilting arm preferably is a cantilever arm that is supported at oneend portion by said tilting shaft inside the inner eccentric sleeveshaft and at another end portion carries the shutter. The shutter may beof any appropriate type, preferably the shutter is a conical, spherical,parabolic or flap type valve shutter.

Preferably, the one or more eccentric sleeve shafts, as well as thetilting shaft within the integrated dual-motion shutter-actuating deviceare rotationally mounted with axially spaced bearings.

With the disclosure a number of advantages can be achieved compared toexisting solutions, among which the most important benefits are:

-   -   During the opening of the shutter, particles on the shutter can        fall off due to the tilting motion.    -   Due to the fact the integrated dual-motion shutter-actuating        device is working only with rotational movements, the gas        tightness can easily be achieved with axial shaft gaskets. For        comparison, a translational movement of a cylinder in a dusty        environment has a short life time due to the fact that during        actuation, dust is constantly entering the seals and damaging        the sealing surfaces.    -   There is no loss of working height during opening motion of the        shutter.    -   The major part of the mechanism can easily be placed outside of        the valve casing.    -   With one eccentric sleeve shaft a constructionally simple        solution can be provided which fits most situations, especially        when primary motion starts with only a vertical component (axes        A and B in a same horizontal plane, see also FIGS. 1 and 3).    -   With two eccentric sleeve shafts, the tilting arm is        pivot-mounted in the inner eccentric sleeve shaft. The inner        eccentric sleeve shaft is pivot mounted in the outer eccentric        sleeve shaft. The outer eccentric shaft is pivot-mounted in the        outer sleeve or casing. With two eccentric sleeve shafts with        opposite eccentricity position and equal eccentricity a uniform        and purely translational movement (horizontal/vertical) of a        shutter can be realized when both eccentric sleeve shafts are        actuated simultaneously in opposite directions during the        unclamping/clamping motion.

BRIEF DESCRIPTION OF THE DRAWINGS

A preferred embodiment of the disclosure will now be described, by wayof example, with reference to the accompanying drawings in which:

FIG. 1A-C is a series of partial vertical cross sectional views of afirst embodiment of a valve sealing arrangement showing the integrateddual-motion shutter-actuating device with one eccentric sleeve shaft;

FIG. 2 is a series of partial vertical cross sectional views of anembodiment such as depicted in FIG. 1 showing the valve sealingarrangement within its casing;

FIG. 3A-C is a series of partial vertical cross sectional views of asecond embodiment of a valve sealing arrangement showing the integrateddual-motion shutter-actuating device with one eccentric sleeve shaftwith a preferred arrangement of associated actuators;

FIG. 4A1-B2 is a series of cross sectional views of a third embodimentof a valve sealing arrangement showing the integrated dual-motionshutter-actuating device with two eccentric sleeve shafts; and

FIG. 5A-C is a series of back views of a fourth embodiment of a valvesealing arrangement showing the integrated dual-motion shutter-actuatingdevice with one eccentric sleeve shaft of an alternative actuatorarrangement with one primary motion actuator and a tilting control rod.

Further details and advantages of the present disclosure will beapparent from the following detailed description of several not limitingembodiments with reference to the attached drawings.

DETAILED DESCRIPTION

FIG. 1A-C is a series of partial vertical cross sectional views of afirst embodiment of a valve sealing arrangement 10 showing theintegrated dual-motion shutter-actuating device with one inner eccentricsleeve shaft 20. In FIG. 1A, the shutter 40 mounted on one end of thetilting arm 30 is in the closed position firmly seated on valve seat 50.The integrated dual-motion shutter-actuating device comprises astationary outer cylindrical sleeve 25 in which an inner eccentricsleeve shaft 20 is rotationally mounted with means of bearings 26. Theinner eccentric sleeve shaft 20 can be rotated around central axis A bymeans of eccentric crank 21 to which it is connected.

Within the offset bore of the inner eccentric sleeve shaft 20 thecylindrical shaft connected at one end to tilting arm 30 and at theother end to tilting crank 31 is mounted with means of bearings 36 torotate about axis B when tilting crank 31 is actuated.

The eccentricity in the embodiment of FIG. 1A-C is the distance betweencenters A and B. As a non-limiting example, in common sealing valvearrangements, the eccentricity will generally be chosen to be between 50and 200 mm, preferably between 80 and 120 mm. In the closed position inFIG. 1A axis B is located in a vertical plane perpendicular to tiltingdirection comprising axis C of sealing valve (seat) 50. Stationary axisA is situated laterally from movable axis B (also called eccentricityposition herein).

The primary motion is effected by rotating eccentric sleeve shaft 20 bymoving eccentric crank 21 from the position shown in FIG. 1A to that inFIG. 1B. At the very beginning of the unclamping motion, shutter 40moves almost vertically down, essentially parallel to the axis C of thevalve seat (see also description of FIG. 2 below). The extent of theinitial almost vertical distance can be controlled by the eccentricity,the larger the eccentricity the greater the almost straight initialdistance. In fact, in practice, the most important moment in terms ofwear of the seat and gasket are the first few millimeters of the primarymotion. Indeed, in common cases, the gaskets are firmly compressed inthe sealed closed position of the shutter. Such gaskets have heights ofcompressibility of a few millimeters, such as approximately 3 mm. So ifin such a case the shutter has been lowered by these 3 mm from the seat,there is no more contact between shutter and seat and thus thesubsequent motion can be chosen more freely. During the primary motion,eccentric sleeve shaft 20 is turned by an angle of 90° counterclockwiseand the path of moving axis B (and thus of the shutter) is a quadrantwith a radius equal to the eccentricity until axis B is below axis A inFIG. 1B. Shutter 40 is now at a distance from the valve seat which issufficient to start the secondary motion of tilting the tilting arm 30with shutter 40 to a lateral parking position as illustrated in FIG. 1C.

The tilting operation (secondary motion) is effected by rotating thetilting shaft around axis B by means of an actuator (not represented)turning tilting crank 31 counterclockwise at a sufficient angle to clearthe passage of the valve.

The initial almost straight vertical movement of a one eccentricdual-motion mechanism as described herein is further illustrated in FIG.2. FIG. 2 illustrates a sealing valve arrangement essentially asdescribed in connection with FIG. 1A-C within a housing 60. The curvereferenced P_(p) and P_(s) represents the path taken by any point of theshutter (such as its center) during primary motion (P_(p)) and secondarymotion (P_(s)). As can be seen P_(p) initially only has a verticalcomponent, which is generally advantageous to reduce wear of the valveseat, sealing gaskets and shutter.

It is to be noted that if wear is not a (main) issue, the initialposition of axis B in FIG. 1A could be chosen at a location higher orlower than axis A knowing that in such cases the initial movement willhave both a vertical and an horizontal component which result in abiased unsealing of the shutter from the valve seat. By choosing aninitial position which is higher than in FIG. 1A, the distance of theshutter from the valve seat will be greater, the maximum distance beingtwice the eccentricity (see also above).

FIG. 3A-C show an arrangement similar to that of FIG. 1A-C, but with apreferred actuating mechanism. Primary motion actuator 22, e.g. ahydraulic jack, is fixed to a stationary mounting point on one end andto crank 21 on the other. By actuating actuator 22, eccentric sleeveshaft 20 is rotated to a position as illustrated in FIG. 3B. In theembodiment of FIG. 3A-C, the secondary motion (tilting) actuator 32 isconnected at one end to a control rod assembly with a control rod 33, alever 34 pivoting about a stationary point 35. The aim of the controlrod assembly is to maintain the shutter arm 30 essentially verticalduring the primary motion. As eccentric crank 21 is moved, control rod33 acts on lever 34 pivoting around point 35, the lever acting on oneend of actuator 32 in such a way as to keep shutter arm 30 verticalduring primary motion. When primary motion is terminated, actuator 32turns tilting shaft via tilting crank 31 to lift the shutter 40 in aparking position as illustrated in FIG. 3C.

In a non-illustrated embodiment of the sealing valve arrangement,secondary motion actuator 32 can be mounted (similarly to actuator 22)to a stationary point at one end and to tilting crank 32 at the other.It is noteworthy that maintaining the shutter arm vertically during theprimary motion is not essential. Furthermore, even if desired, it can beachieved by other means such as by controlling the orientation of thetilting shaft by way of its actuator 32.

FIGS. 4A1 and B1 show a schematic cross section of a sealing valvearrangement wherein the integrated dual-motion shutter-actuating devicecomprises an inner 201 and an outer 202 eccentric sleeve shaft in anouter cylindrical sleeve 25. Both eccentrics have the same eccentricity.As a non-limiting example, in common sealing valve arrangements, eacheccentricity will generally be chosen to be between 20 and 100 mm,preferably between 30 and 60 mm. Tilting shaft 37 connected at one endto the tilting arm 30 is rotationally held within the bore of the innereccentric sleeve shaft 201. FIGS. 4A1 and B1 represent the position ofthe shutter before and after the primary motion, i.e. with the shutterin a sealed closed position in sealing contact with the valve seat (A1)and an open position unclamped from the valve seat (B1). FIGS. A2 and B2depict the same situation as a transverse cross-section through theintegrated dual-motion shutter-actuating device.

By rotating inner and outer eccentric sleeve shafts 201 and 202simultaneously but in opposite directions the center of the tiltingshaft is moved along a straight path by a distance equal to the sum ofthe eccentricities if each eccentric is rotated by 90° or even up totwice the sum of eccentricities if the angular rotation is 180° for eacheccentric sleeve shaft.

FIG. 5A-C show an arrangement similar to that of FIG. 1A-C, but with analternative embodiment of the integrated dual-motion shutter-actuatingdevice. A primary motion actuator (not shown), e.g. a hydraulic jack, isfixed to a stationary mounting point on one end and to crank 21 on theother. By actuating the primary motion actuator, eccentric sleeve shaft20 is rotated to a position as illustrated in FIG. 5B. In the embodimentof FIG. 5A-C, the secondary motion (tilting) actuator 32 is a controlrod which is pivotally connected at one end to a stationary point and atthe other end to the tilting shaft 37 or its associated crank 31. Aseccentric crank 21 is moved, control rod 32 acts on tilting shaft 37(via tilting crank 31) to lift the shutter 40 in a parking position asillustrated in FIG. 5C.

The invention claimed is:
 1. A sealing valve arrangement for a shaftfurnace charging installation, said arrangement comprising: a shutterarranged for cooperating with a valve seat; an integrated dual-motionshutter-actuating device for moving said shutter between a sealed closedposition in sealing contact with the valve seat and an open positionremote from the valve seat, said integrated dual-motionshutter-actuating device comprising: a primary motion assembly formoving said shutter from said sealed closed position to an unclampedposition wherein the shutter is released from the valve seat; asecondary motion assembly for tilting said shutter from said unclampedposition to said open position remote from the valve seat, saidsecondary motion assembly comprising a tilting arm carrying said shutterand connected to a tilting shaft that defines an axis of rotation and atilting shaft actuator configured to impart an angular rotation aboutsaid axis to said tilting arm; wherein said integrated dual-motionshutter-actuating device further comprises a stationary outercylindrical sleeve, wherein said primary motion assembly comprises aninner eccentric sleeve shaft rotationally mounted within said outercylindrical sleeve and a primary motion actuator configured to impartangular rotation to said inner eccentric sleeve shaft, the primarymotion being a function of the eccentricity and angular rotation of theinner eccentric sleeve shaft; and wherein said tilting shaft of saidsecondary motion assembly is rotationally mounted within said innereccentric sleeve shaft of said primary motion assembly, the secondarymotion being a function of the angular rotation of the tilting shaft. 2.The sealing valve arrangement as claimed in claim 1, wherein the innereccentric sleeve shaft is arranged within the outer cylindrical sleevesuch that its eccentricity position is located laterally by about aneccentricity distance from the center of the outer cylindrical sleevewhen the shutter is in the sealed closed position.
 3. The sealing valvearrangement as claimed in claim 1, wherein said primary motion assemblyfurther comprises an outer eccentric sleeve shaft rotationally mountedwithin said outer cylindrical sleeve, wherein said inner eccentricsleeve shaft is rotationally mounted within said outer eccentric sleeveshaft, the primary motion being a function of the eccentricity andangular rotation of both inner and outer eccentric sleeve shafts.
 4. Thesealing valve arrangement as claimed in claim 3, wherein inner and outereccentric sleeve shafts have the same eccentricity, and wherein aneccentric actuator is configured to impart a simultaneouscounter-rotating angular rotation to said inner and outer eccentricsleeve shafts.
 5. The sealing valve arrangement as claimed in claim 1,wherein said tilting arm is a cantilever arm that is supported at oneend portion by said tilting shaft and at another end portion carries theshutter.
 6. The sealing valve arrangement as claimed in claim 1, whereinsaid shutter is a conical, spherical, parabolic or flap type valveshutter.
 7. The sealing valve arrangement as claimed in claim 1, whereinthe eccentric sleeve shaft(s) are rotationally mounted with axiallyspaced bearings.